Lubrication means for service pump drive on compressors



July 8, 1952 M. HAEBERLEIN LUBRICATION MEANS FOR SERVICE PUMP DRIVE oN coMPREssoRs 3 Sheets-Sheet l Filed May 6, 1949 NKDMmWKL XNJADD 1 w. ILA!! oo IUFISW ...P-2 1- July 8, 1952 M. HAEBERLEIN 2,602,583

LUBRICATION MEANS FOR SERVICE PUMP DRIVE oN COMPRESbORS Filed May 6, 1949 5 Sheets-Sheet 2 i 67 95 |05 59 S7 99 V 1 MAX H A E B ERLEI N F'l 2 INVENT'OR MXL-7M# July 8, 1952 v M. HAEBERLEIN 2,602,583

LUBRICATION MEANS FOR SERVICE PUMP DRIVE ON COMPRESSORS Filed May 6' 1949 l sheets-sheet s ll A HE7/A \,\l W" 2 y @s 53 5556 gf le 38 67 34- 52 MAX HAEBERU-:IN INVENT0R- FIG-.4

Patented July 8, 1952 UNITED 'sTArss LUBICATION MEANS FOR SERVICE BUMP DRIVE ON COlVIPRESSORS l Max'Haeberlein, Maplewood, N. J., assigner to vWorthington Pump and Machinery Corpora-.r tion.. IarrisornN... J., a corporation of Delaware estimation May t. 1949,y serial No.. 91.707

`end of the compressor rotor and the pump itself.

The present invention embodies lubrication means. for the said driving and coupling means by utilizing lubricant beingireturned'for recirculation and lubricantxbeing forced upward 'from the pump itself.

Accordingly, it is an object of the present ine vention to provide a simple lubricating .means for the service pump drive in a compressor.

It is, another object of the present invention to provide lubrication for the service pump drive wherein the return lubricant operates to furnish a portion of the. lubrication -forfthe more inacoessible parts thereof.

Itis another object. oi the. present'invention to provide a means. .for lubrioatingthe'servioe pump drive which. utilizes the return lubricant; acting by gravity flow through proper chambers and. passages to lubricate all portions thereof properly.

lt, is a further object of the present invention to utilize the service pump itself to furnish means for forcing lubricant upwardly along that portion of the drive which is connected directly to the Pump With these and other objects in view, as may appearv from the accompanying specification, the invention consists of various features of construction and combination ofpparts, which will be first described in connection with the accompanying drawings, showing'a lubrication means vfor service pump drive oncompressorsof a preferred form embodying .the inventi'on,`` and the features forming the invention will'be specifically pointed out inthe claims. In the drawings:` f f Figure 1 is a diagrammatic. sketch showing a typical compressor system. 1 f

Figure 2 is a partial section .of thev outboard end of a centrifugal compressor.

Figure 3 is an enlarged section .of the. invene tion. f e

Figure i. is an enlarged section of the lower portion of: the invention.

8 Claims. (Cl. 230.-.207)

Referring to the drawings, Figure 1 illustrates a diagrammatic sketch of a typical compressor system showing generically a casing I having aA rotor shaft 2 connected by a coupling 3 to step-up gears 4 connected in turn to a prime mover (not shown) which may be any suitable type for-operating the compressor I. The step-up gears il and the coupling 3 may also be of any suitable type easily purchasable Aon the open market and are therefore generically indicated. The'rotor' shaft 2 provided'vfor the compressor I has a line bearing 5 at the inboard end and a thrust bearing- 6 at the outboard end to allow for relatively frictionless rotation of the rotor shaft 2 and to provide inner sealing means during operation. It

being understood that while this type of com.-v

pressor is shown and described that any typical compressor utilizing a lubrication'system having a similar form of driving means as hereinafter described would sufce to describe this invention.

The lubrication means for the service pump drive operates'in conjunction with the lubrication system for the compressor which is indicated in Figure 1, and forms an integral part of the supporting structure and passages of the driving and coupling means for the service pump as hereinafter described.

Figure 2 shows a fully enclosed oil 'or lubricant reservoir l formed by an upper portion 8 and a lower or sump portion 9 mounted on the out? board or thrust bearing end of the compressor I. A balance line I0 is provided to balance the oil pressure in the reservoir 'I. It communicates at one end with a filter chamber II having a strainer i2 therein which is located in theupper portion 8 of' the reservoir 1, and at the other end.`

opens into the suction inlet I3 of the compressor I. The strainer I2 preventingtthe escape of oil vapor which develops in the reservoir l, due to escape of the gas compressed in .the compressor and trapped in the lubricant where it. comes in contact therewith and the whirling of the driving and coupling means therein.

The lower or sump portion 9 carries. the

lubrication system ,starting up, shuttingdown or in case of failure of the service pump I 4. An automatic pressure switch (not shown) being provided to start the auxiliary pump motor I1 when the pressure in the service pump I4 falls below a predetermined level.

The driving and coupling means for the service pump I4 is clearly shown in Figures 2, 3, and 4 of the drawings. The axial portion being illustrated in Figures 2 and 3 showing a fragment of rotor" shaft 2 passing through the casing I 8 of the compressor I at the outboard or thrust bearing end and extending into the upper portion 6. The end of the rotor shaft 2 is threadably engaged by a nut I9 to which an adapter plate 20 is fixedly connected by suitable means such as bolts 2 I. A

first toothed coupling member 22 is in turn fixedly connected to the adapter plate by suitable means such as a nut 23, and engages one end of a flexible tube-like sleeve 24 having lands 25 and downs 26 for contact with the toothed portion of the coupling member 22. A second toothed coupling member 21 engages the other end of said flexible sleeve 24, being in turn fixedly connected by suitable means such as a nut 28 to a pinion shaft 29 having a first spiral bevel gear 30 formed in the outer end thereof.

The pinion shaft 29 passes through a bore 3I substantially larger than said shaft 29 formed in a pinion support member 32 and is supported therein by identical thrust bearings 33 and 34 mounted at either end of said bore 3| whereby an elongated annular space 35 will be formed in the said bore.

Pinion support member 32 is substantially cylindrical in construction and is provided with a. flange-like portion 36 for engagement' with a U-shaped cuplike'horizontal support 31 struck from an outer disc cover plate 38" connected by suitable means such as bolts 39 in fluid tight engagement to the upper portion 8 of the reservoir 1 and forming an integral part thereof whereby the cover plate 38, horizontal support 31 and the pinion supportv 32 will form a lower chamber 40. A short horizontal upper support 4I spaced above said U-shaped support 31 is also struck from the cover plate 38 and forms means whereby a closure member 42 supported by the upper support 4I and the U-shaped support 31 will close the lower chamber 40 and prevent oil vapor, or excess oil from being thrown up into the strainer I2 in the filter chamber II. It being understood that while the support members 31 and 4I are shown as being struck from the cover plate 38 that they may be formed as an integral part of the upper portion 8 to accomplish the same purpose.

An upper chamber 43 is mounted on the pinion support member 32 in a substantially vertical plane above the bore 3| inwardly of the flangelike portion 36 and having a portion thereof formed by the flange itself. The upper chamber 43 will receive lubricant therein from the lubrication systeml by means hereinafter described. n

The upper chamber 43 is provided with a vertical passage 44 extending downwardly and opening into the elongated space 35 above described for passing lubricant by gravity flow thereto and a horizontal passage 45 extending outwardly through the flange-like portion 36. An elongated member 46 is slidably and adjustably mounted in that portion of the U- shaped support member 31 in the axial line of the horizontal passage 45 and is provided with a bore 41 which communicates at one end with the horizontal passage and has an opening 48 at the other end into the lower chamber whereby lubricant fluid will also pass by gravity flow from the upper chamber to the lower chamber.

Elongated member 46 may be adjustably set at a desired axial position by-a` set screw 49 threadably mounted in the 'U-shaped. support 31 for engagement with a groove on the outer' circumference of the elongated member 46 so that lubricant fluid will flow out of opening 48 over the rstspiral bevel gear 30 which is formed on the end of the pinion shaft 29 which extends through the bore 3I whereby the first spiral bevel gear 30 will be in the lower chamber. Thus lubricant fluid will collect in the lower chamber to further lubricate additional portions of the driving and coupling means. An overflow 5I is provided to prevent the level of the lubricant from rising in the lower chamber as this would place the lubricant inthe path of 'the gear train in the lower chamber and cause the lubricant to be whipped into a froth, overflow thechamber and prevent proper lubrication.

To lubricate the pinion shaft 29 thrust bearings 33 and 34, identical vin construction, are provided withlongitudinal'slots v52 on the'inner contact-- ing surface which communicate with the elongated annular space 35 attheir inner ends and with radial slots 53 at vtheir outer ends.

Thrust bearing 33 operates -to furnish lubrication for the flexible coupling sleeve 24 and the coupling members 22 and 21. The Aradial'slots thereon communicating with-an annular groove 54 in the second coupling member 21 which is in turn connected to a series of axial passages 55A opening into the inner portion `56 of'the flexible sleeve 24 to provide the lubrication needed there- Thrust bearing 34 operates to pass'lubricant fluid by gravity flow through the 'longitudinal slots 52 and the radial slots 53 to the lower chamber 40 in addition to the opening 43'in the elongated member 46 above described. 'v

The vertical portion of the driving and coupling means is clearly shown in Figuresr 3 and 4 of the drawings and includes anV intermediate shaft 51 held in position as hereinafter described.

Figure 3 shows the U-shaped support member 31 with an opening 58 having a step bearing support 59 mounted therein by means of a flange 60 thereon engaging an annular recess 6I on the inner or chamber surface 62 of the U-shaped support member, by suitable means such as bolts 63.

'I'he step bearing support 59 is substantially cylindrical in shape and is provided with a vertical bore 64 therethrough. The upper portion of the vertical bore 64 receives a step bearing 65 and the lower portion of the bore receives the upper end of an oil pump sleeve 66 which extends upwardly into the bore 64 just short of the'step bearing whereby an annular passage 61 will be formed therebetween.

The step bearing 65 is xedly connected to `the step bearing support 53 by suitable'means such as bolts 68 to prevent movement thereof. Annular shims 69 are provided to 'position the step bearing 65 at the most desirable point for holding the shaft 51 in position. Step bearing 65 is further provided with vertical slots 1I] `and transverse slots 1I communicating with the annular passage v61 at one end and opening -into the lower chamber 40 at the other end to allow lubricant fluid to flow from the lower chamber 40 by gravity flow to the annular passage 61 between the step bearing 65 andk the upper portion of the oil pump sleeve 66.

Intermediate shaft 51 passes looselythrough oil pump sleeve 66 extending upwardly and downwardly therewith whereby a cylindrical passage 1'2 will be formed having the upper end communicating with the annular passage -61form-ed in the bore 64. Lubricant fluid can, therefore, by gravity flow, pass from the lower chamber 40 through the transverse passages 1| and vertical passages into the annular passage 6.1 to pass thence downwardly into the cylindrical passage 12 providing lubrication for the more inaccessible portions of the driving and coupling means.

The shaft 51 extends upwardly past the oil pump sleeve 66- in the bore by means of a continuous upper extension 13 of aV lesser circumference than the shaft 51, in substantially surface-to-surface engagement with the step bearing 65 into the lower chamber 40V where a second spiral bevel gear 14 is xedly connected thereto by suitable means such as a nut 15 threadably engaging the upper extension 13 of the shaft 5.1.

The second bevel gear 14 is positioned to be engaged and rotated by the rst spilal bevel gear 30 and by adjusting the setting of the stepy bearing 65 by means of the annular shims 69 will be securely positioned on the upper surface by contact with the rst spiral bevel gear 30 and on the under surface by contact with the step bearing 65. Accordingly, the shaft 51 which is fixedly connected to. the second' spiral bevel gear 14 will also be held in position obviating the necessity of having a xed lower connection with the service pump I4.

Shaft 51 and oil pump sleeve 66 extend downwardly `through the lower or sump portion 9 of the reservoir 1, to be received in an elongated cylindrical space 16 provided in the main service pump I4. A tongue and slot arrangement 11 or other suitable means is provided so that the shaft* 51 will be connected to the rotary gear shaft 18 of rotary gear 19 which extends upwardly into the cylindrical space 16 and into a portion i of the oil pump sleeve 66 to meet the shaft 51.

A portion of the cylindrical space 16 forms a small chamber 8.0 in the upper portion of the service pump I4, which communicates with theA cylindrical passage 12 formed around the shaft 51 by the oil-pump sleeve 66. A cross passage 8| Vin the service pump I4 opening at one end into the chamber 80 communicates with the bearing chamber 82 of a second rotary gear `|33 so that lubricant fluid forced therein by the rotation of the rotaryv gears 19 and 83 will be forced through the cross-passage 8| into the chamber 80 and thence upwardly into the cylindrical passage 12 to contact the lubricant fluid descending therealong by gravity flow to providelubrication vfor shaft 51 and the working parts connected thereto. y

Thus, when the compressor is started the rotor shaft 2 will transmit lrotary motion in the axial line thereof through the flexible sleeve 24 and the coupling members 22 and 21 to the pinion shaft 29 and accordingly to the first spiral bevel gear 30. First spiral bevel gear 30 will in turn engage and drive the second spiral bevel gear 14 which in turn transmits the motion to the vertical portion comprising the upper extension 19 and the shaft 51 in contact. with the rotary gear 19 by means of the tongue and slot arrangement 11 with the rotary gear shaft A19 whereby rotaryr the. service. pump 4.,

When the servicepump I4 isrotated as above described, lubricant fluid. in the `reservoir- 1 will be drawn into. the opening 84 on .the service pump I4,V shown in, Figure l, and delivered to. the lubrication system at high pressure entering conduit 8,5 `provided with a check valve 86 therein for controlling the. direction of flow in the said conduit. Lubricant is forced through the conduit i; to. a four-Way by-pass valve 8l into. a. lter member 0.8.. It is returned from the lter member 88' to the by-pass valve 81 and is then passed simultaneously to a pressure control assembly 8.9 prm/ided to lov-pass a quantity of oil. backY to the reservoir to maintain a nxed quantity therein. to. protect the bearings of the service. pump 4' and to Aan oil cooler 9,0. It is led from the cooler A90. to thev high pressure fluid linev 9|'. High pressure line 9| conducts the lubricant to various portions of the compressor which utilize the high pressure lubricant such as the thrust bearing 6', line. bearing. 5, etc., which are supplied by their respective lines 92 and 93, etc., all of'which is clearly shownl in Figure l ofthe drawings.

Line 92 leading high pressure lubricant to the thrust bearing 9, is connected by means of a flange 9'4to the inlet end' 95.01 a passage 96 by suitable means such as'bolts 91. Passage 96 communicates with a milled recess 98 in the thrust bearing 6 which is provided with two drilled holes 99 and |00 connected to an annular groove |0| on the inner or surface contacting portion of the thrust bearing 6. Oil grooves |02 are provided between the thrust collar |03 and the thrust bearing 6 which communicate between the annular groove |0I and an annular space |04 whereby lubricant will pass from the passage 96 which receives the lubricant from line 92 to the annular space |04 via the milled recess 98, the drilled holes 99 and |00,v annular grooves IOI and oil grooves |02.

Lubricant received in the annular grooves |0| will also pass alongl the inner surface of the thrust bearing 6 to provide lubrication for the rotor when the compressor is operating. Exit ports |05 are provided in the thrust bearing B for returning this lubricant to the reservoir by ygravity flow as is clearly shown in Figure 2 of the drawings.

On the upper side of the annular space |04 an outlet port |06 is provided which communicates with a return passage |01 which receives lubricant therein from the annular space |04 passing it to the connecting passage |08 communicating 1n turn with the discharge passage |09 opening over the upper chamber 43 whereby lubricant is delivered to the upper chamber 43 and flows by 'gravity flow to the various portions of the driving and coupling means as above described.

While one form of the invention has been illustrated, it will be understood that the invention is not to be limited to the specic construction or arrangements of parts shown, but that they may be widely modified Within the invention defined by the claims.

What is claimed is:

1. In a lubricating means for the service oil pump drive on elastic fluid compressors, a casing for said compressor with a rotor shaft therein, an enclosed lubricant reservoir connected to said casmg 1ncluding an upper portion and a lower portion forming said reservoir, and means providing communication with the suction side of the compres-scr, the rotor shaft passing through said` casing into the upper portion'of the reservoir, a thrust bearing for said .rotor shaft where it passes through said casing, said compressor having a lubrication system including a service oil pump carried by the lower portion of theireservoir, driving and coupling means mounted in said upper portion and extending into said lower. portion of the reservoir to connect said rotor shaft to said service oil pump for driving said pump when the compressor is in operation to furnish lubricant at high pressure to the lubricating system, a conduit in said lubricating system for supplying lubricant to the lower side of said thrust bearing, means on the upper side of said thrust bearing to allow lubricant to pass to the driving and coupling means in the upper portion of the reservoir, an oil pump sleeve about that portion of the driving and coupling means connected to said service oil pump and forming an annular cylindrical passage therebetween communicating at one end with said second mentioned means, to receive lubricant uid therein by gravity ow, and passages in said serviceoil pump adapted to receive lubricant fluid under pressure therefrom communicating with the lower portion of said annular cylindrical passage to force oil upwardly to meet the lubricant fluid flowing downwardly therein for lubricating the portion of the driving and coupling means connected to said service oil pump. f

2. In a lubricating means for the service -oil pump drive on elastic fluid compressors, a casing for said compressorV with a rotor shaft therein, an enclosed lubricant reservoir connected to said casing including an upper portion and a lower portion forming said reservoir, and means providing communication with the suction side of the compressor, the rotor shaft passing through said casing into the upper portion of the reservoir, a thrust bearing for said rotor shaft where it passes through said casing, said compressor having a lubrication system including a service oil pump carried by the lower portion of the reservoir, driving and coupling means mounted in said upper portion and extending into said lower portion of the reservoir to connect said rotor shaft to said service oil pump for driving said pump when the compressor is in operation to furnish lubricant at high pressure to the lubricating system, a conduit in said lubricating system for supplying lubricant to the lower side of said thrust bearing, an annular passage about said thrust bearing connected at the lower side thereof to said conduit for receiving lubricant fluid therein, passage means formed in said upper portion 'of the reservoir communicating with said annular passage at one end, chamber means mounted on said driving means communicating with 'the other end of said passage means to receive lubricant uid therefrom, distributing means coacting with said chamber means for lubricating the driving and coupling means in the upper portion of said reservoir, an oil pump sleeve about that portion of the driving and coupling means connected to said service oil pump and forming an annular cylindrical passagetherewith communicating at one end with said distributing means to receive lubricant iiuid therein by gravity flow, and passages in said service oil pump adapted to receive lubricant yfluid under pressure therefrom communicating'with the lower portion ofv said annular cylindrical passage to force oil upwardly to meet the lubricant fluid flowing -downwardly therein for lubricating the portion of the driving and coupling means connected to said service oil pump. l

3. In a lubricating means for the` service oil pump drive on elastic fluid compressors as claimed in claiin,2 wherein said chamber means mounted on the driving and coupling means in the upper portion of the reservoir includes, a first chamber to coact with said passage means to receive lubricant therein, supports for said driving and coupling means adapted to form a second chamber disposed to receive lubricant by gravity flow from said first chamber. distributing means between said first chamber and said second chamber to pass lubricant from said first chamber to said second chamber and disposed to lubricant over said driving and coupling means by gravity flow, means to direct lubricant from said second chamber to lubricate a portion of said driving means extending downwardly therefrom, and overflow means in said second chamber to regulate the level of lubricant therein.

4. In a lubricating means for the service oil pump drive on elastic fluid compressors as claimed in claim 2 wherein said distributing means includes vertical and horizontal exit ports in said rst chamber,` at least one of said horizontal exit ports adjustably mounted on said rst chamber to deliver lubricant flow directly to said second chamber byv gravity vow, and at least one of said vertical exit ports adapted to furnish lubricant fluid to said driving and coupling means by gravity ilow.

5. In a lubricating means for the service oil pump drive on elastic fluid compressors, a casing for said compressor with a rotor shaft therein, an enclosed lubricant reservoir connected to said casing including an upper portion and a lower portion forming said reservoir, and means providing communication with the suction side of the compressor, the rotor shaft passing through said casing into the lupper portion of said reservoir, a thrust bearing for said rotor shaft where it passes through said casing, said compressor having a lubrication system including a service oil pump carried by said lower portion of the reservoir, driving and coupling means mounted in said upper portion and extending into said lower portion to connect said rotor shaft to said service oil pump for driving said pump when the compressor is in operation to furnish-lubricant at high pressure to said lubrication system, a conduit in said lubrication system for supplying lubricant to the lower side of said thrust bearing, an annular passage about said thrust bearing connected at the lower side thereof to saidconduit for receiving lubricant uid therein, passage means formedin said upper portion of the reservoir communicating with said annular passage to allow lubricant to be passedv to the upper portion of said reservoir, a rst chamber to coact with said passage means to receive lubricant therein, supports for said driving and coupling means adapted to ,form a second lchamber-disposed to receive lubricant by gravity flow from said irst chamber, Vertical and horizontal exit ports in said first chamber, at least one of said horizontal exit ports adjustably mounted on said rst chamber to deliver lubricant fluid to said second chamber directly by gravity flow, atleast one of said vertical exit ports adapted to furnish lubricant fluid to said driving and coupling: means disposed in the upper portion of said reservoir, an oil pump sleeve connected at one end to said second chamber and at the other'end to said service oil pump, saidpump sleeve loosely surroundc. i9. c ing said driving 'means extending downwardly into theilower portion of the reservoir whereby an vannular cylindrical passage Tis formed about said drivingmea-ns, a thrust bearing for said driving means'extending downwardly Ainto said lowerportion mounted in said second chamber, passages in said thrust bearing -having-one-end communicating will;v said second chamberzand the other end communicating with said .annular cylindrical passage to allow lubricant to pass by gravity flow downwardly into said annular chamber to lubricate said driving means extending downwardly, passages in said oil pump communicating with the lower portion of said'annular cylindrical passage adapted to receive lubricant under pressure from said service oil pump whereby the lubricant will be forced upwardly into the lower portion of said annular cylindrical passage to meet lubricant flowing downwardly therein for lubricating the driving and coupling means connected to said service oil pump, and an overow opening in said second chamber to control the level of returning lubricant and to provide means for returning ex- A cess uid to the lower portion of the reservoir.

6. In a lubricating means for the service oil pump drive on elastic fluid compressors, a casing for said compressor with a rotor shaft therein, an enclosed lubricant reservoir connected to said casing including an upper portion and a lower portion forming said reservoir, and means providing communication with the suction side of the compressor, the rotor shaft passing through said casing into the upper portion of said reservoir, a thrust bearing for said rotor shaft where it passes through said casing, said compressor having a lubrication system including a service oil pump carried by said lower portion of the reservoir, driving and coupling means mounted in said upper portion and extending into said lower portion to connect said rotor shaft to said service oil pump for driving said pump when the compressoiis in operation to furnish lubricant at high pressure to said lubrication system, a conduit in said lubrication system for supplying lubricant to the lower side of said thrust bearing, an annular passage about said thrust bearing connected at the lower side thereof to said conduit for receiving lubricant fluid therein, passage means formed in said upper portion of the resn ervoir communicating with said annular passage to allow lubricant to be passed to the upper portion of said reservoir, a nrst chamber to coact with said passage means to receive lubricant therein, supports for said driving and coupling means adapted to form a second chamber disposed to receive lubricant by gravity flow from said rst chamber, vertical and horizontal exit ports in said rst chamber, at least one of said horizontal exit ports adjustably mounted cn said first chamber to deliver lubricant fluid to said second chamber directly by gravity flow, at least one of said vertical exit ports adapted to furnish lubricant uid to said driving and coupling means disposed in the upper portion of said reservoir, an annular chamber formed in said support structure about the driving means to receive lubricant fluid from at least one of said vertical exit ports, means communicating with said annular chamber on one side thereof to allow lubricant fluid to pass to said coupling structure, means communicating with the other side of said annular chainber to allow fluid to pass to said second chamber by gravity flow, an oil pump sleeve about that portion of the driving and coupling means connected to said service oil pump and forming an acoace annular ycylindrical passage therebetween communicating with the second chamber at the upper end thereof to receive lubricant iiuid 'by gravity now from said second chamber, passages in said service oil .pump adapted to receive lubricant fluid under pressure therefrom communicating with the lower portionof said vannular cylindrical passage to force oil upwardly to meet lubricant fluid nowing downwardly therein :for lubricating the portion of the driving and coupling means connected to the service oil pump, and an overflow opening in said second chamber to control the level of lubricant fluid and to provide means for returning excess fluid to the reservoir.

7. In a lubricating means for the service oil pump drive on elastic fluid compressors, a casing for said compressor with a rotor shaft therein, an enclosed lubricant reservoir connected to said casing including an upper portion and a lower portion forming said reservoir, and means providing communication with the suction side of the compressor, the rotor shaft passing through said casing into the upper portion of said reservoir, a

l thrust bearing for said rotor shaft where it passes through said casing, said compressor having a ylubrication system including a service oil pump carried by said lower portion of the reservoir, support members formed in the said upper portion of the reservoir, driving and coupling means in axial alignment with said rotor shaft and connected thereto mounted in said support structure, driven means vertically mounted in said support structure and connected between said driving means and said pump to transmit rotatory motion to said pump for operation in the lubrication system, a conduit in said lubrication system for supplying lubricant to the lower side of said thrust bearing, an annular passage about said thrust bearing connected at the lower side thereof with said conduit for receiving lubricant iiuid therein,

passage means formed in said upper portion of the reservoir communicating with said annular passage to allow lubricant to be passed to the upper portion of said reservoir, a first chamber to coact with said passage means to receive lubricant therein, a second chamber substantially adjacent said rst chamber formed by said support members disposed to receive lubricant by gravity flow from said rst chamber, vertical and horizontal exitports in said first chamber, a rst portion of said axial driving means mounted in said upper portion of said res-ervoir outside of said second chamber, a second portion oi said axial driving means mounted inside said second chamber, said vertical exit ports for lubricating said first portion outside said second chamber, said horizontal exit ports for lubricating said second portion inside said second chamber an oil pump sleeve about said driven means connected to said service oil pump and forming an annular cylindrical passage therebetween communicating at its upper end with said second chamber to receive lubricant fluid by gravity flow therefrom, passagesJ in said service oil pump adapted to receive lubricant under pressure therefrom communicating with the lower portion of said annular cylindrical passage to force oil upwardly to meet the lubricant uid owing downwardly therein for lubricating the driven means connected to the service oil pump, and an overflow opening in said second chamber to control the level of lubricant iiuid and to provide means for returning excess fluid to the reservoir.

8. In a lubricating means for the service oil pump drive on elastic fluid compressors as claimed 1'1 in claim 7 wherein atleast one of said horizontal exit` ports will be adjustably mounted on said first chamber to reach inaccessible portions of said axial driving means inside said second chamber.

MAX HAEBERLEIN.

REFERENCES CITED The following references are of record in the le of this patent:

Number o 1,575,970 1,607,318

Number 12 UNITED STATES PATENTS I Name Date Carrier Mar."9, 1926 Spillman Nov. 16,1926 McIntyre May 7. 1929 FOREIGN PATENTS Y Country Date France vJuly 21. 1924 

